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WO2019159502A1 - Dispositif de régulation de fluide - Google Patents

Dispositif de régulation de fluide Download PDF

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Publication number
WO2019159502A1
WO2019159502A1 PCT/JP2018/044654 JP2018044654W WO2019159502A1 WO 2019159502 A1 WO2019159502 A1 WO 2019159502A1 JP 2018044654 W JP2018044654 W JP 2018044654W WO 2019159502 A1 WO2019159502 A1 WO 2019159502A1
Authority
WO
WIPO (PCT)
Prior art keywords
main plate
plate
main
fluid control
opening
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2018/044654
Other languages
English (en)
Japanese (ja)
Inventor
伸拓 田中
近藤　大輔
宏之 横井
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Murata Manufacturing Co Ltd
Original Assignee
Murata Manufacturing Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Murata Manufacturing Co Ltd filed Critical Murata Manufacturing Co Ltd
Priority to JP2019518318A priority Critical patent/JP6536770B1/ja
Priority to GB2008177.4A priority patent/GB2582485B/en
Publication of WO2019159502A1 publication Critical patent/WO2019159502A1/fr
Priority to US16/943,301 priority patent/US11391275B2/en
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B45/00—Pumps or pumping installations having flexible working members and specially adapted for elastic fluids
    • F04B45/04—Pumps or pumping installations having flexible working members and specially adapted for elastic fluids having plate-like flexible members, e.g. diaphragms
    • F04B45/047—Pumps having electric drive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/003—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by piezoelectric means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B43/00—Machines, pumps, or pumping installations having flexible working members
    • F04B43/02—Machines, pumps, or pumping installations having flexible working members having plate-like flexible members, e.g. diaphragms
    • F04B43/04—Pumps having electric drive
    • F04B43/043—Micropumps
    • F04B43/046—Micropumps with piezoelectric drive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves

Definitions

  • the present invention relates to a fluid control device that controls the flow rate of a fluid.
  • Patent Document 1 describes a fluid control device including a pump chamber and a valve chamber.
  • the pump chamber includes a top plate that is a part of the valve chamber and a vibration plate to which the drive body is directly attached.
  • the top plate and the vibration plate vibrate in opposite phases to control the fluid. Yes.
  • an object of the present invention is to suppress vibration of the center of gravity of the fluid control device.
  • the fluid control device includes a valve and a pump.
  • the valve includes a first main plate, a second main plate having one main surface facing one main surface of the first main plate, and a side plate connecting the first main plate and the second main plate, the first main plate and the second main plate. And a valve chamber surrounded by side plates.
  • the first main plate has a first opening communicating with the inside and outside of the valve chamber
  • the second main plate has a second opening communicating with the inside and outside of the valve chamber.
  • a valve membrane capable of switching between a state in which the first opening and the second opening are in communication and a state in which the first opening and the second opening are not in communication is disposed in the valve chamber. Has been.
  • the pump is disposed to face the other main surface of the second main plate, and includes a piezoelectric element, a vibration part including the vibration plate, and a pump chamber formed by the second main plate.
  • the pump chamber communicates with the valve chamber through the second opening.
  • the frequency coefficient of the first main plate is larger than the frequency coefficient of the second main plate.
  • the first main plate having a large frequency coefficient has higher rigidity than the second main plate. Therefore, the first main plate and the vibrating part are displaced in opposite phases, and work in the direction in which the vibration of the fluid control device accompanying the vibration of the vibrating part is canceled. For this reason, the fluctuation of the gravity center position of the fluid control device is reduced, and the reliability of the fluid control device is improved.
  • the fluid control device includes a valve and a pump.
  • the valve includes a first main plate, a second main plate having one main surface facing one main surface of the first main plate, and a side plate connecting the first main plate and the second main plate, the first main plate and the second main plate. And a valve chamber surrounded by side plates.
  • the first main plate has a first opening communicating with the inside and outside of the valve chamber
  • the second main plate has a second opening communicating with the inside and outside of the valve chamber.
  • a valve membrane capable of switching between a state in which the first opening and the second opening are in communication and a state in which the first opening and the second opening are not in communication is disposed in the valve chamber. Has been.
  • the pump is disposed to face the other main surface of the second main plate, and includes a piezoelectric element, a vibration part including the vibration plate, and a pump chamber formed by the second main plate.
  • the pump chamber communicates with the valve chamber through the second opening.
  • the first main plate and the second main plate are made of the same material.
  • the first main plate is thicker in the main surface direction than the second main plate.
  • the first main plate and the vibration part vibrate in opposite phases. Therefore, it works in the direction in which the vibration of the fluid control device accompanying the vibration of the vibration part is canceled. This improves the reliability of the fluid control device.
  • the first main plate and the diaphragm are displaced in opposite phases.
  • the first main plate and the vibration part vibrate in opposite phases. Therefore, the influence of the vibration of the vibration unit on the center of gravity of the apparatus and the influence of the vibration of the first main plate on the center of gravity of the apparatus work in the direction to be canceled, thereby improving the reliability of the fluid control apparatus.
  • the first main plate of the fluid control device according to the present invention is provided with an external housing to which the valve is fixed.
  • the fluid control device of the present invention is used for medical equipment.
  • the medical device is, for example, a sphygmomanometer, a massager, an aspirator, a nebulizer, and a negative pressure closure therapy device.
  • FIG. 1A is an external perspective view from the valve 20 side of the fluid control apparatus 10 according to the first embodiment of the present invention.
  • FIG. 1B is an external perspective view from the pump 30 side of the fluid control apparatus 10 according to the first embodiment of the present invention.
  • FIG. 2 is an exploded perspective view of the fluid control apparatus 10 according to the first embodiment of the present invention.
  • FIG. 3 is a side sectional view of the fluid control apparatus 10 according to the first embodiment of the present invention.
  • 4 (A) to 4 (F) are image diagrams showing fluctuations in the position of the center of gravity in the side cross-sectional view of the fluid control apparatus 10 according to the first embodiment of the present invention.
  • FIG. 5 is a graph showing the displacement rate with respect to the frequency coefficient ratio of the fluid control apparatus 10 according to the first embodiment of the present invention.
  • FIG. 6 is a graph showing the rate of change of the center of gravity variation with respect to the frequency coefficient ratio of the fluid control apparatus 10 according to the first embodiment of the present invention.
  • FIG. 7 is a side cross-sectional view of the fluid control apparatus 10 according to the first embodiment of the present invention in which a structure including the valve 20 and the pump 30 is fixed to an external housing.
  • FIG. 1A is an external perspective view from the valve 20 side of the fluid control apparatus 10 according to the first embodiment of the present invention.
  • FIG. 1B is an external perspective view from the pump 30 side of the fluid control apparatus 10 according to the first embodiment of the present invention.
  • FIG. 2 is an exploded perspective view of the fluid control apparatus 10 according to the first embodiment of the present invention.
  • FIG. 3 is a side cross-sectional view taken along line SS of the fluid control device 10 in FIGS. 1 (A) and 1 (B).
  • FIG. 4 (A) to 4 (F) are image diagrams showing fluctuations in the position of the center of gravity in the side cross-sectional view of the fluid control apparatus 10 according to the first embodiment of the present invention.
  • FIG. 5 is a graph showing the relative displacement with respect to the frequency coefficient ratio of the fluid control apparatus 10 according to the first embodiment of the present invention.
  • FIG. 6 is a graph showing the variation rate of the center of gravity with respect to the frequency coefficient ratio of the fluid control apparatus 10 according to the first embodiment of the present invention.
  • FIG. 7 is a side cross-sectional view of the fluid control device 10 according to the first embodiment of the present invention in which a structure including the valve 20 and the pump 30 is fixed to an external housing.
  • symbol is abbreviate
  • the fluid control device 10 includes a valve 20 and a pump 30.
  • a plurality of first openings 201 are formed on the top surface side of the bulb 20.
  • the first opening 201 is a vent hole.
  • the valve 20 includes a first main plate 21, a second main plate 22, a side plate 23 and a valve membrane 24.
  • the thickness t1 of the first main plate 21 is greater than the thickness t2 of the second main plate 22.
  • the first main plate 21 and the second main plate 22 are discs.
  • the side plate 23 is a cylinder.
  • the side plate 23 is disposed between the first main plate 21 and the second main plate 22 and connects the first main plate 21 and the second main plate 22 so as to face each other. More specifically, the centers of the first main plate 21 and the second main plate 22 coincide in plan view.
  • the side plate 23 connects the peripheral edges of the first main plate 21 and the second main plate 22 arranged in this way over the entire circumference.
  • the valve 20 has a valve chamber 200 that is a cylindrical space surrounded by the first main plate 21, the second main plate 22, and the side plates 23.
  • the side plate 23 may be integrally formed with the first main plate 21 or the second main plate 22.
  • the first main plate 21 or the second main plate 22 may have a recessed shape.
  • the valve membrane 24 is disposed in the valve chamber 200.
  • a plurality of first openings 201 are formed in the first main plate 21 so as to penetrate the first main plate 21.
  • the valve membrane 24 is formed with a plurality of second openings 202 penetrating the valve membrane 24 so as to overlap each of the plurality of first openings 201 in plan view.
  • a plurality of third openings 203 are formed in the second main plate 22 so as to penetrate the second main plate 22.
  • the plurality of third openings 203 are formed at positions that do not overlap the first openings 201 and the second openings 202 in plan view. Through the plurality of third openings 203, the valve chamber 200 of the valve 20 and the pump chamber 300 of the pump 30 communicate with each other.
  • the pump 30 is formed using the second main plate 22 as one component.
  • the pump 30 is formed by the second main plate 22, the pump side plate 31, the pump bottom plate 32, and the vibrating portion 33.
  • the vibration part 33 is formed by a vibration plate 331 and a piezoelectric element 332.
  • the thickness of the diaphragm 331 is assumed to be t3.
  • the pump bottom plate 32 and the diaphragm 331 are integrally formed. More specifically, when the pump 30 is viewed in plan from the second main plate 22 side, the pump bottom plate 32 and the diaphragm 331 are connected via the connecting portion 35 so as to be flush with each other. In other words, along the periphery of the pump bottom plate 32, the pump bottom plate 32 and the diaphragm 331 are formed so as to have a plurality of pump bottom openings 34 that are not connected to each other with a predetermined opening diameter. With this configuration, the diaphragm 331 is held by the pump bottom plate 32 so as to vibrate.
  • the pump side plate 31 has an annular shape in plan view from the first main plate 21 side.
  • the pump side plate 31 is disposed between the second main plate 22 and the pump bottom plate 32, and connects the second main plate 22 and the pump bottom plate 32. More specifically, the centers of the second main plate 22 and the pump bottom plate 32 coincide in plan view.
  • the pump side plate 31 connects the peripheral edges of the second main plate 22 and the pump bottom plate 32 arranged in this way over the entire circumference.
  • the pump 30 has a pump chamber 300 that is a cylindrical space surrounded by the second main plate 22, the pump bottom plate 32, and the pump side plate 31.
  • the piezoelectric element 332 includes a disc-shaped piezoelectric body and a driving electrode.
  • the driving electrodes are formed on both main surfaces of the disk piezoelectric body.
  • the piezoelectric element 332 is disposed on the opposite side of the diaphragm 331 from the pump chamber 300 side, that is, on the outside of the pump 30. At this time, the center of the piezoelectric element 332 and the center of the diaphragm 331 substantially coincide with each other in plan view.
  • the piezoelectric element 332 is connected to a control unit (not shown).
  • the control unit generates a drive signal for the piezoelectric element 332 and applies it to the piezoelectric element 332.
  • the piezoelectric element 332 is displaced by a drive signal, and stress due to this displacement acts on the diaphragm 331. Thereby, the diaphragm 331 is flexibly vibrated. For example, the vibration of the diaphragm 331 generates a waveform of the first type Bessel function.
  • the volume and pressure of the pump chamber 300 change as the vibration plate 331 (vibration unit 33) bends and vibrates.
  • the fluid sucked from the pump bottom opening 34 is discharged from the third opening 203.
  • valve membrane 24 moves to the first main plate 21 side by the fluid flowing in from the third opening 203. As a result, the fluid is discharged to the outside through the second opening 202 and the first opening 201. On the other hand, when fluid tries to flow from the third opening 203 to the pump bottom opening 34, the valve membrane 24 moves to the second main plate 22 side and closes the third opening 203. Therefore, it functions as the fluid control device 10 having a rectifying function.
  • the first main plate 21 and the second main plate 22 are made of a material and a thickness that can vibrate in a direction orthogonal to the main surface.
  • the material of the first main plate 21 and the second main plate 22 is, for example, stainless steel.
  • the first main plate 21 and the second main plate 22 are used by using a frequency coefficient which is a specific calculation formula. Compare.
  • the frequency coefficient is a coefficient indicating the flexibility of the first main plate 21 and the second main plate 22 that vibrate. More specifically, using the plate thickness t of the diaphragm, the longitudinal elastic modulus (Young's modulus) E, and the material density ⁇ of the diaphragm, the following expression is used.
  • the frequency coefficient F1 of the first main plate 21 is The frequency coefficient F2 of the second main plate 22 becomes larger. That is, the first main plate 21 is less flexible than the second main plate 22.
  • FIG. 4A to 4 (F) show images representing fluctuations in the position of the center of gravity using the side cross-sectional views of the fluid control device 10.
  • FIG. 4A to 4F description will be made using the thickness t1 of the first main plate 21 and the thickness t2 of the second main plate 22.
  • the position of the center of gravity is an example.
  • 4 (A) to 4 (C) are fluctuation image diagrams of the conventional configuration. At this time, the thickness t1 of the first main plate 21 and the thickness t2 of the second main plate 22 are equal.
  • FIG. 4 (D) to FIG. 4 (F) are fluctuation image diagrams of the present embodiment.
  • the thickness t 1 of the first main plate 21 is larger than the thickness t 2 of the second main plate 22.
  • FIGS. 4 (A) to 4 (F) in order to make the drawings easier to understand, some configurations and some reference numerals are omitted, and the vibration state is exaggerated.
  • FIG. 4A is an image diagram when the fluid control apparatus 10 is stopped. At this time, the gravity center position of the fluid control device 10 is P1.
  • FIG. 4B is an image diagram when the fluid control device 10 sucks the fluid. At this time, the center of gravity position P2 of the fluid control device 10 is greatly shifted toward the first main plate 21 side.
  • FIG. 4C is an image diagram when the fluid control apparatus 10 discharges the fluid. At this time, the gravity center position P3 of the fluid control device 10 is greatly shifted toward the second main plate 22 side.
  • the center of gravity position P2 is the first main plate 21 side when the center of gravity position P1 when the fluid control apparatus 10 is stopped (in the case of FIG. 4A) is used as a reference.
  • the center-of-gravity position P3 is greatly shifted toward the second main plate 22 side.
  • FIG. 4D is an image diagram when the fluid control device 10 is stopped. At this time, the gravity center position of the fluid control device 10 is P4.
  • FIG. 4E is an image diagram when the fluid control apparatus 10 sucks fluid. At this time, the gravity center position P5 of the fluid control device 10 is substantially the same position as the gravity center position P4.
  • FIG. 4F is an image diagram when the fluid control device 10 discharges the fluid. At this time, the gravity center position P6 of the fluid control device 10 is substantially the same position as the gravity center position P4.
  • the center of gravity position P5 and the center of gravity position P6 are based on the center of gravity position P4 when the fluid control apparatus 10 is stopped (in the case of FIG. 4D). Are substantially the same position.
  • the thickness t1 of the first main plate 21 is larger than the thickness t2 of the second main plate 22, so that the position of the center of gravity can be made substantially the same when the fluid control device 10 vibrates.
  • the frequency coefficient F1 is larger than the frequency coefficient F2
  • the center of gravity position can be made substantially the same position. That is, a large vibration at the center of gravity is suppressed. Therefore, when the structure including the valve 20 and the pump 30 is attached to another member, the stress applied to the attached position is reduced due to the change in the center of gravity. Thereby, the reliability of the fluid control apparatus 10 is improved.
  • FIG. 5 is a graph showing a simulation result of the displacement rate with respect to the frequency coefficient ratio in the fluid control apparatus 10.
  • the thickness t2 of the second main plate 22 is 0.5 mm
  • the thickness t3 of the diaphragm 331 is 0.4 mm.
  • the thickness t1 of the first main plate 21 is changed between 0.3 mm and 0.7 mm.
  • the horizontal axis is the frequency coefficient ratio.
  • the frequency coefficient ratio is expressed by (frequency coefficient of first main plate 21) / (frequency coefficient of second main plate 22).
  • the vertical axis represents relative displacement.
  • the relative displacement is represented by the displacement of the first main plate 21 with respect to the vibration plate 331 or the displacement of the second main plate 22 with respect to the vibration plate 331 on the basis of the displacement of the vibration plate 331.
  • the first main plate 21 When the relative displacement is 0% or more, the first main plate 21 is displaced in the same phase with respect to the diaphragm 331. When the relative displacement is smaller than 0%, the first main plate 21 is displaced in an opposite phase with respect to the diaphragm 331.
  • the first main plate 21 and the vibration plate 331 vibrate in the same phase. Further, when the thickness t1 of the first main plate 21 ⁇ the thickness t2 of the second main plate 22, the first main plate 21 and the vibration plate 331 vibrate in opposite phases.
  • the vibration of the first main plate 21 and the vibration of the vibration plate 331 are in opposite phases.
  • phase difference ⁇ is in the range of 120 ° ⁇ ⁇ 240 °, the center-of-gravity vibration suppressing effect can be obtained. If it is in the range of 152 ° ⁇ ⁇ 208 °, the center-of-gravity vibration can be halved, and the effect is greater.
  • the phase difference ⁇ can be measured with a displacement meter using a laser Doppler method or the like.
  • a hole may be formed in the external housing that fixes the fluid control device 10.
  • the measurement location is the surface of the piezoelectric element 332 on the vibration plate 331 side, and the measurement on the first main plate 21 side is in the vicinity of the hole. Even when a measurement hole is opened in the external housing, the vibration state is not affected.
  • FIG. 6 is a graph showing a simulation result of the rate of change of the center of gravity variation with respect to the frequency coefficient ratio in the fluid control apparatus 10.
  • the thickness t2 of the second main plate 22 is 0.5 mm
  • the thickness t3 of the diaphragm 331 is 0.4 mm.
  • the thickness t1 of the first main plate 21 is changed between 0.3 mm and 0.7 mm.
  • the horizontal axis is the frequency coefficient ratio.
  • the frequency coefficient ratio is expressed by (frequency coefficient of first main plate 21) / (frequency coefficient of second main plate 22).
  • the vertical axis represents the rate of change of the center of gravity vibration.
  • the center-of-gravity variation change rate is the ratio of vibration canceled by the first main plate 21 or the second main plate 22 to the vibration of the diaphragm 331.
  • the center displacement amplitude A1 of the first main plate 21, the center displacement amplitude A2 of the second main plate 22, and the center displacement amplitude A3 of the diaphragm 331 are in phase with the diaphragm 331, they are positive values. Further, the center displacement amplitude A1 of the first main plate 21, the center displacement amplitude A2 of the second main plate 22, and the center displacement amplitude A3 of the diaphragm 331 are negative values when they are opposite in phase to the diaphragm 331.
  • the rate of change in the center of gravity vibration is a positive value, it means that the center of gravity vibration is amplified by the first main plate 21 and the second main plate 22. Conversely, if the rate of change in the center of gravity vibration is a negative value, it means that the center of gravity vibration has been reduced by the first main plate 21 and the second main plate 22.
  • the center-of-gravity vibration change rate becomes a positive value, and the center-of-gravity vibration is amplified. Further, when the thickness t1 of the first main plate 21 ⁇ the thickness t2 of the second main plate 22, the center-of-gravity vibration change rate becomes a negative value, and the center-of-gravity vibration is reduced.
  • the vibration of the center of gravity of the fluid control device 10 is reduced and the reliability is improved.
  • FIG. 7 is a side cross-sectional view in which the structure including the valve 20 and the pump 30 is fixed to the external housing in the fluid control apparatus according to the present embodiment.
  • the 1st main board 21 has the extending part 25 which extended itself.
  • the fluid control device 10 is fixed to the first external housing 40 via the extending portion 25.
  • casing is formed by arrange
  • the structure of the fluid control device 10 is disposed in a space surrounded by the first external housing 40 and the second external housing 50.
  • the vibration of the center of gravity of the fluid control device 10 is reduced. For this reason, even if the 1st main board 21 is being fixed to the 1st external housing
  • the structure may be fixed to the second main plate 22.
  • the vibration displacement of the first main plate 21 is smaller than the vibration displacement of the second main plate 22, if the structure is fixed to the first main plate 21, the reliability is further improved.
  • the external casing is formed of the first external casing 40 and the second external casing 50 .
  • the external housing may be formed integrally or may be configured by combining three or more housings.
  • the outer casing only needs to have a shape that can fix the structure, and the shape of the outer casing is not limited to this.
  • the shape of the valve 20 and the pump 30 of the fluid control device 10 has been described as a substantially disk-shaped configuration.
  • the shape of the valve 20 and the pump 30 of the fluid control device 10 is not limited to a disk shape, and may be a shape close to a polygon.
  • first main plate 21 and the second main plate 22 are described as being made of the same material and made of stainless steel or the like. However, the first main plate 21 and the second main plate 22 are not limited to the same material. The flexibility of the first main plate 21 can be obtained, and the same effect can be obtained by using a material whose frequency coefficient is larger than that of the second main plate 22.
  • the fluid control device described above is used for medical devices such as a blood pressure monitor, a massage device, a suction device, a nebulizer, and a negative pressure closure therapy device. Thereby, the efficiency of a medical device can be improved.
  • the first main plate and the second main plate have been described using main plates having a constant thickness.
  • the average values of the thicknesses of the main plates are compared, and (average thickness t1a of the first main plate 21)> (the second main plate 22 You may comprise so that it may become average thickness t2a).

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)

Abstract

La présente invention concerne un dispositif de régulation de fluide (10) comprenant une soupape (20) et une pompe (30). La soupape (20) comporte une chambre de soupape (200). Une première plaque principale (21) présente une première partie ouverture (201) à travers laquelle communiquent l'intérieur et l'extérieur de la chambre de soupape (200), et une seconde plaque principale (22) présente une seconde partie ouverture (202) à travers laquelle communiquent l'intérieur et l'extérieur de la chambre de soupape (200). Une soupape (24) capable de commuter l'état de communication est disposée à l'intérieur de la chambre de soupape (200). La pompe (30) comporte un élément piézoélectrique (332) et une chambre de pompe (300). La chambre de pompe (300) communique avec la chambre de soupape (200) par l'intermédiaire de la seconde partie ouverture (22). Pendant la vibration de flexion d'une partie vibrante (33), le coefficient de fréquence de la première plaque principale (21) est supérieur au coefficient de fréquence de la seconde plaque principale (22).
PCT/JP2018/044654 2018-02-16 2018-12-05 Dispositif de régulation de fluide Ceased WO2019159502A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
JP2019518318A JP6536770B1 (ja) 2018-02-16 2018-12-05 流体制御装置
GB2008177.4A GB2582485B (en) 2018-02-16 2018-12-05 Fluid control apparatus
US16/943,301 US11391275B2 (en) 2018-02-16 2020-07-30 Fluid control apparatus

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2018025663 2018-02-16
JP2018-025663 2018-02-16

Related Child Applications (1)

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US16/943,301 Continuation US11391275B2 (en) 2018-02-16 2020-07-30 Fluid control apparatus

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WO2019159502A1 true WO2019159502A1 (fr) 2019-08-22

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PCT/JP2018/044654 Ceased WO2019159502A1 (fr) 2018-02-16 2018-12-05 Dispositif de régulation de fluide

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GB (1) GB2582485B (fr)
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TWI720878B (zh) * 2020-04-24 2021-03-01 研能科技股份有限公司 致動傳感模組

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JP5928160B2 (ja) * 2012-05-29 2016-06-01 オムロンヘルスケア株式会社 圧電ポンプおよびこれを備えた血圧情報測定装置
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JP2015117647A (ja) * 2013-12-19 2015-06-25 東芝テック株式会社 圧電ポンプおよび圧電ポンプを備えるインクジェット記録装置
JP2017072140A (ja) * 2014-07-16 2017-04-13 株式会社村田製作所 流体制御装置

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